EP0040864A2 - Power shift transmission - Google Patents
Power shift transmission Download PDFInfo
- Publication number
- EP0040864A2 EP0040864A2 EP81105647A EP81105647A EP0040864A2 EP 0040864 A2 EP0040864 A2 EP 0040864A2 EP 81105647 A EP81105647 A EP 81105647A EP 81105647 A EP81105647 A EP 81105647A EP 0040864 A2 EP0040864 A2 EP 0040864A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- gear
- input
- drive means
- transmission
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H3/097—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts the input and output shafts being aligned on the same axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
- F16H2003/007—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths with two flow paths, one being directly connected to the input, the other being connected to the input though a clutch
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
- This invention relates to transmissions adapted for power shifting and in particular for use in land vehicles.
- It is known in the transmission art to first synchronize and clutch an intermediate shaft or ratio gear with the transmission output and to then clutch the intermediate shaft or ratio gear to the transmission input. Such synchronizing, which may be referred to as output synchronizing, is also known in prior art transmissions having plural countershafts. Many prior art transmissions, which employ plural countershafts and output synchronizing, power shift from one countershaft to another to upshift or downshift the transmission and synchronize a non-driving countershaft with the transmission output in preparation for the next shift.
- A power shift transmission of this type and in accordance with the preamble of
claim 1 is known e.g. from US-patent 3 001 413 or from DE-C 935 047. This transmission is provided with two multiple ratio power paths which are alternately connected between a main drive input and an output shaft. Each of the power paths includes synchronizing means and means operative subsequent to the synchronizing for positively clutching the synchronized elements. Furthermore friction clutch means in the form of a double-acting friction clutch are provided which are located between the constantly driven drive means and the two medial input shafts so that alternately one of the drive- or input shafts is connected to the drive means. - When the above prior art transmissions are used in combination with a torque converter,the sole source of power input to the transmission is - through the torque converter which is rather inefficient and not needed in the higher speed ratios of the transmission. To negate this inefficiency, torque converter bypass or lock-out clutches have been used in practice. Such clutches have the disadvantage in that they and their needed control systems may increase the cost and complexity of the transmissions.
- It is therefore an object of the invention to provide a transmission suited for use in combination with a torque converter and which is low in initial cost and economical in us while it is readily shifted without a break in power between the transmission input and output. This object is obtained by the invention as it is characterized in the claims.
- The features of the invention are very significant for providing a transmission embodying the starting and shifting advantages inherent in a torque converter while at the same time avoiding the inherent inefficiencies of the torque converter in high speed ratio gears.
- The preferred embodiment of the invention is shown in the accompanying drawings in which:
- FIGURE 1 is a schematic view of the transmission, looking in the direction of arrows 1-1 of FIGURE 2;
- FIGURE 2 is a schematic view of the transmission, looking in the direction of arrows 2-2 of FIGURE 1;
- FIGURE 3 is a detailed view of the transmission of FIGURE 1, looking in the direction of arrows 1-1 of FIGURE 2;
- FIGURE 4 is a detailed view of a portion of the transmission, looking in the direction of arrows 3-3 of FIGURE 2; and
- FIGURE 5 is a schematic view of a portion of a countershaft assembly of FIGURES 1 and 3.
- Certain terminology referring to direction and motion will be used in the following description. The terminology is for convenience in describing the preferred embodiment and should not be considered limiting unless explicitly used in the claims.
- Looking first at FIGURE 1, therein is schematically illustrated a power
shift transmission assembly 10 adapted for use in an unshown land vehicle, but not limited to such use.Transmission 10 is preferably automatically shifted by an unshown control system, which control system forms no part of the instant invention.Transmission 10 includes aninput shaft 12 which may be directly driven by an unshown internal combustion engine, ahousing assembly 14, atorque converter assembly 16, a ratiochange gear assembly 18 which is driven byinput shaft 12 throughtorque converter assembly 16 in first, second, and reverse ratios and is driven directly by abypass input shaft 13 in third and fourth ratios, and anoutput shaft 20 axially aligned withinput shafts - The
torque converter assembly 16 is conventional in that it includes a fluid coupling of the torque converter type having animpeller 22a driven byinput shaft 12 through ashroud 24, a turbine 22b hydraulically driven by the impeller and in turn driving asleeve shaft 26 which extends intogear assembly 18, and a runner or stator 28 which becomes grounded tohousing 14 via a one-way roller clutch 30 carried by asleeve shaft 32 fixed tohousing assembly 14. Shroud 24 also drives apump 34 for pressurizing the torque converter, for lubricating the transmission, and for selectively pressurizing friction clutches ingear assembly 18. - Sleeve 26 provides a fluid power or torque converter driven shaft for first, second, and reverse ratio gears in
gear assembly 18.Bypass shaft 13 is in continuous direct drive withinput shaft 12 and provides a torque converter bypass for driving third and fourth ratio gears; this arrangement of the bypass shaft negates the need of a separate torque converter bypass clutch. - Looking now at FIGURES 1 and 2, the schematically illustrated ratio change gear assembly includes two
countershaft assemblies shafts Assembly 36 includes ashaft 40 rotatably supported at its ends 40a and 40b byhousing assembly 14, a double actingsynchronizer clutch 42, first and thirdspeed ratio gears shaft 40, and a hydraulically actuatedfriction clutch 48. Firstspeed ratio gear 44 is driven by and in continuous mesh with aninput drive gear 50 which is non-rotatably secured tobypass shaft 13. Synchronizerclutch 42 may be a conventional double acting synchronizer having aclutch member 54 at one end which is non-rotatably secured togear 44, aclutch member 56 at the other end which is non-rotatably secured togear 46, and acenter clutch member 58 at the center which is non-rotatably secured toshaft 40.Center clutch member 58 may be slidably shifted leftwardly or rightwardly in a conventional manner to, respectively,couple gear shaft 40. Such slidable shifting of the center clutch member first frictionallycouples countershaft 40 with one of the ratio gears and after synchronism is reached, then positively clutches the shaft with the gear via a jaw clutch shown in FIGURE 3.Center clutch member 58 includes a radially extending flange portion 60a which may be gripped by an unshown shift fork to effect the leftward and rightward shifting in a conventional manner.Friction clutch 48 includes ahousing member 62 non-rotatably secured toshaft 40, two sets of interdigitateddisks 64 and 65, and asleeve shaft 66 rotatably supported byshaft 40.Disks 64 are non-rotatably secured tosleeve shaft 66 and disks 6-5 are non- rotatably secured tohousing member 62. Both disk sets are axially moveable inhousing 62 and are frictionally interconnected in response to hydraulic pressure being selectively applied to an unshown piston in thehousing member 62.Sleeve shaft 66 is non-rotatably secured to adrive gear 68 which is rotatably supported byshaft 40.Drive gear 68 is in continuous mesh with anoutput gear 70 which is non-rotatably secured tooutput shaft 20. -
Countershaft assembly 38 differs fromassembly 36 mainly in that it also includes a reverse ratio gear.Assembly 38 includes ashaft 72 rotatably supported at itsends 72a and 72b byhousing assembly 14, a double actingsynchronizer clutch 72, second, fourth and reversespeed ratio gears shaft 72, a hydraulically actuatedfriction clutch 82, and a positive typejaw clutch assembly 84. Clutch 84 may be a synchronized clutch similar toclutches speed ratio gear 76 is driven by and in continuous mesh with aninput drive gear 86 which is non-rotatably secured to torque converter drivenshaft 26. Fourthspeed ratio gear 78 is driven by and in continuous mesh withinput drive gear 52 which is non-rotatably secured tobypass shaft 13. Synchronizerclutch 74 is a double acting clutch and may be identical tosynchronizer 42. Synchronizerclutch 74 includes aclutch member 90 at one end which is non-rotatably secured togear 76, aclutch member 92 at the other end which is non-rotatably secured togear 78, and acenter clutch member 94 at the center which is non-rotatably secured toshaft 72.Center clutch member 94 includes a radially extending flange portion 96a which may be gripped by an unshown shift fork to effect leftward and rightward shifts in the same manner as described forsynchronizer 42.Friction clutch 82 may be identical tofriction clutch 48.Friction clutch 82 includes ahousing member 98 which is non- rotatably secured toshaft 72, two sets ofdisks 100 and 101, and a sleeve shaft 102 rotatably supported byshaft 72. Disks 100 are non-rotatably secured to sleeve shaft 102 anddisks 101 are non-rotatably secured tohousing member 98. Both disk sets are axially moveable inhousing 98 and are frictionally interconnected in response to hydraulic pressure being selectively applied to an unshown piston inhousing member 98. Sleeve shaft 102 is non-rotatably secured to adrive gear 104 which is rotatably supported byshaft 72.Drive gear 104 is in continuous mesh with anoutput gear 106 which is non-rotatably secured tooutput shaft 20. -
Reverse gear 80 is rotatably supported byshaft 72 and is driven by anidler gear assembly 108, seen only in FIGURES 2 and 4. Idlergear assembly 108 includes ashaft 110 which is non-rotatably supported byhousing assembly 14, agear 112 which is rotatably supported onshaft 110 and in continuous mesh withinput drive gear 50 which is driven by torque converter drivenshaft 26, and agear 114 which is rotatably supported onshaft 110 and non-rotatably secured togear 112. Gear 114 is in continuous mesh withreverse gear 80. Jawclutch assembly 84 includesjaw clutch teeth 116 which are non-rotatably secured togear 80 and ajaw clutch member 118 mounted for sliding movement relative toshaft 72 and secured against rotation relative toshaft 72.Member 118 includes jaw clutch teeth 118a which engage withteeth 116 and an annular groove 118b which receives a shift fork 152 engaging the clutch in a conventional manner. Shift fork 152 is shown in FIGURE 3. - By way of example, the ratios of ratio
change gear assembly 18 are: first gear - 4.05, second gear - 2.22, third gear - 1.42, fourth gear - 1.00, and reverse gear - 4.76. As may be seen, bypassshaft 13 andoutput 20 rotate at the same speeds when drive is through fourth gear. -
Gear assembly 18 may also be provided with a direct drive clutch 120 at the confronting ends 13a and 20a and the bypass ofoutput shafts countershaft 38. Such a clutch may be a non-synchronized positive type jaw clutch as illustrated herein, since hereinshafts clutch 120 could be used to provide a fifth speed ratio by decreasing the ratio spacing of first, second, third, and fourth ratio gears so thatoutput shaft 20 would rotate slower thanbypass shaft 13 when driving in fourth speed. When using clutch 120 to provide a fifth speed ratio, the clutch is preferably a fluid actuated friction clutch or a synchronized jaw clutch, both of which may be of a conventional type. - Looking now at FIGURES 3 and 4, therein the transmission of FIGURES 1 and 2 is disclosed in greater detail to show additional features not readily shown in a schematic. The transmission of FIGURES 3 and 4 does not include the direct drive clutch 120 but is otherwise the same as that previously described. Thus, in FIGURES 3 and 4 the numerals corresponding to those of FIGURES 1 and 2 will refer to parts already described.
- In FIGURE 3,
housing assembly 14 includes a front housing member 14a having a bell housing portion 14b formed integral therewith, a rear housing member 14c, and anintermediate plate member 14d.Members 14a, 14c, and 14d are secured together via plurality of bolts 121, one of which is shown. Aflange portion 14e of the bell housing provides means for securing the transmission to the rear of an engine housing.Intermediate plate 14d includes through bores 14f and 14g for the passage ofshafts end 13a ofshaft 13. End 20a ofshaft 20 extends into a blind bore 13b inshaft 13 and is supported therein by a roller bearing 124.Intermediate plate 14d also includes several unshown oil passages for directing lubricating oil to various portions of the transmission and for directing oil to actuateclutches -
Shroud 24 oftorque converter assembly 16 includes a front portion 24a and a rear portion 24b which are non-rotatably secured together at 126. Front portion 24a is integrally formed with a cup shapedportion defining shaft 12 and having internal splines 12a which receive splines 13c for drivingshaft 13. Front portion 24a also includes a plurality of studs 128 for securing the transmission input to an unshown crankshaft or output shaft of an engine or motor. The rear portion 24b is fixed toimpeller 22a at 130 and is welded to a sleeve 132. Sleeve 132 rotatably supports the rear portion 24a via abearing 134 and drives pump 34.Pump 34 may be a well known crescent gear pump. Bearing 134 is supported by pump housing 34a which is bolted to housing portion 14a via a plurality ofbolts 136.Shafts housing assembly 14 viaroller bearings Shafts housing assembly 14 and each other by aball bearing 122 androller bearings 142 and 144. - Looking now at
cross-sectioned countershaft 38, ends 72a and 72b ofshaft 72 are supported byball bearings Reverse gear 80 is rotatably supported onshaft 72 by aroller bearing 150 and includes an axially extending portion 80a having external splines defining jawclutch teeth 116 of the jawclutch assembly 84.Clutch assembly 84 further includes a ring member 151 splined on its I.D. toshaft 72 and splined on its O.D. to jaw clutch teeth 118a ofmember 118. Annular groove 118b inmember 118 receives a shift fork 152 which is slidably connected to ashift rod 154 of anactuator 156.Actuator 156 includes a piston portion 154a formed on or fixed torod 154 and disposed in a cylinder 14i cast intointermediate plate 14d, and an end plate 158 for closing the cylinder. Aspring 159 disposed between asnap ring assembly 160 and shift fork 152 resiliently urges clutch teeth J18a into engagement withclutch teeth 116 in response to leftward movement ofrod 154 and piston 154a. Asnap ring 162 contacts the shift fork for disengaging the jaw clutch in response to rightward movement of the rod and piston. Cylinder 14i is provided with oil on both sides of piston l54a by unshown passages inintermediate plate 14d. Hydraulic sealing of the piston and cylinder is provided by O-ring seals in a conventional manner. Hydraulic actuators for shiftingsynchronizers -
Gear 76 includes an axially extending sleeve portion 76a having external jaw clutch splines 76b which receive internal splines ofclutch member 90.Gear 76 and sleeve portion 76a are rotatably supported onshaft 72 by a pair of roller bearings 164. In a like manner,gear 44 ofcountershaft assembly 36 includes anaxially extending portion 44a, but of longer length, splined toclutch member 54 and unshown roller bearings for rotatably supporting the gear and sleeve portion onshaft 40. In a similar manner,gear 78 is rotatably supported onshaft 72 by a roller bearing 166 and includes an axially extending portion having external jaw clutch splines 78a which receive internal splines ofclutch member 92.Gear 46 is rotatably mounted onshaft 40 and connected toclutch member 56 in the same manner. - Double acting
synchronizer 74, of whichmembers sleeve 167 splined on its I.D. toshaft 72 and on its O.D. to internal jaw clutch splines 96b of a slidable positive typejaw clutch member 96 integrally formed with flange portion 96a, a pair of friction cone rings 168 and 170 rigidly secured together by three circumferentially positionedpins 172, and a pair of internal friction cone surfaces 90a and 92a which are engageable with external cone surfaces defined byrings 168 and 170.Pins 172, which extend through three chamfered openings 96c circumferentially positioned in flange 96a, have at their centers (the position of the flange in its neutral position) an annular groove 172a having chamfered ends. The I.D. of each chamfered opening 96c is slightly greater than the major O.D. of eachpin 172. Annular grooves 172a are slightly wider than the flange. Centerclutch member 94 further includes threeaxially split pins 174 extending through three chamfered openings 96d which are alternately spaced between openings 96c.Pins 174 each consist of a pair of semicylindrical halves which are biased apart by aleaf spring 176. Each pair of semicylindrical halves define an annular groove 174a having chamfered ends. Annular groove 174a is formed by a semiannular groove defined by each pin half.Spring 176 biases the semiannular grooves outward into engagement with openings 96d. The I.D. of openings 96d is slightly greater than the major O.D. ofpins 174. Annular grooves 174a closely fit the width of flange 96a. - The center
clutch member 94 is shown in the neutral position, therefor both gears 76 and 88 are disengaged, the friction cone surfaces are slightly spaced apart, pins 172 and 174 and their respective grooves are concentric with openings 96c and 96d, and the semiannular grooves defining grooves 174a are biased into engagement with holes 96d. When it is desired to couplegear 76 toshaft 72, flange portion 96a is moved axially to the left by an appropriate shift mechanism. Such movement, which is transmitted throughsplit pins 174, shifts the cone surface of cone ring 168 into contact with cone surface 90a. This contact (providedgear 76 and flange 96a are not synchronous with each other) causespins 172 to move out of concentric alignment with openings 96c, whereby the chamfers of the openings 96c and the chamfers of the grooves 172a engage and prevent further axial movement of the flange due to torque at the interface of the chamfers. As synchronous speeds are reached, the torque at the interface of the chamfers diminishes and the axial force on flange 96a movespins 172 back into a concentric relationship with openings 96c, thereby allowing flange 96a andjaw member 96 to move axially to the left for engaging jaw clutch splines 96b with jaw clutch splines 76b.Gear 78 is coupled toshaft 72 in the same manner by moving the flange rightward. - The transmission gears are preferably helical gears and as such they are axially loaded with substantial forces when they are transmitting torque. Further, since the gears are in continuous mesh, they rotate at different speeds. Hence, it is preferred that the gears be axially isolated from each other to prevent the transmittal of the axial forces across surfaces rotating at different speeds to reduce wear and energy losses. Isolation and axial retention of
gears -
Gear 80 is retained against axial movement relative toshaft 72 in the leftward direction by athrust plate 178 and in the rightward direction through ring member 151 by a shoulder 72c defined by a step inshaft 72. Shoulder 72c prevents axial loading being imposed ongear 76 whengear 80 is engaged.Gear 76 is retained against axial movement relative toshaft 72 in the leftward direction through ring member 151 by a snap ring 180 and in the rightward direction throughring member 167 which abuts a shoulder 72d defined by a step inshaft 72.Gear 78 is retained against axial movement relative toshaft 72 in the leftward direction throughring member 167 by a snap ring 182 and in the rightward direction by a thrush plate 184. -
Friction clutch 82, which is structurally and functionally conventional and identical to clutch 48, includes thehousing member 98 splined toshaft 72 at 98a, the set ofdisks 101 which are slidably splined to internal splines 98b defined by the housing member, the set of disks 100 which are slidably splined to external splines 102a defined by an extension of sleeve 102, areaction member 186 which is non-rotatably secured tohousing member 98 by splines 98b, apiston 188 for squeezing the disks together in response to pressurized fluid being introduced into a chamber 190 defined byhousing member 98 andpiston 188, and a return spring 192 for retracting the piston.Housing member 98 is axially retained by a shoulder 72e defined by a step inshaft 72 and asnap ring 194. Sleeve 102 andgear 104 are rotatably supported onshaft 72 by a pair of roller bearings 196 and are axially retained bysnap rings thrust bearings - The
gear 68 andclutch 48 ofcountershaft assembly 36 are rotatably and axially retained onshaft 40 in a similar manner. -
Output shaft 20 is rotatably supported by the roller bearing 124 and aball bearing 206. The outer race 206a of bearing 206 is supported by housing portion 14c and is axially retained thereto by a shoulder 14k and a snap ring 208. Axial retention ofshaft 20 is provided by the inner race 206b of bearing 206 which is sandwiched between a shoulder 20b defined byshaft 20 and aspacer sleeve 210.Sleeve 210 is held in place by an output yoke 212 which is splined toshaft 20 and axially retained by abolt 214. Output gears 70 and 106 are splined toshaft 20 and are retained in the leftward direction by a flange portion 20c defined byshaft 20 and in the rightward direction by the inner race 206b. - In reviewing the operation, it will be assumed that the
transmission 10 is installed in a land vehicle having an internal combustion engine, that the engine crankshaft is connected to torque converter shroud 24 -by studs 128, that the crankshaft rotates the shroud clockwise when viewing the shroud from the front, and that a shift control system will automatically effect shifting to the desired speed ratios in the proper sequence. Such control systems are well known and are often made responsive to parameters such as engine load and vehicle speed. It will also be assumed that the control system includes a shift control lever which is selectively placed in neutral to disengage the transmission, or in drive to effect forward movement of the vehicle, or in reverse to effect reverse movement of the vehicle. The shift control system referred to herein is by way of example only and does not form part of the invention herein or any preferred form of a control system. - With the shift control lever in neutral and the engine running,
bypass shaft 13 and torque converter drivenshaft 26 rotate clockwise and rotate input drive gears 50, 86, and 52 clockwise, whereby driven gears 44, 46, 76, 78 rotate counterclockwise andgear 80 rotates clockwise since it is driven throughidler gear assembly 108. Further,countershafts synchronizers clutches - Assuming now that a vehicle operator places the shift control lever in drive and wishes to'accelerate the vehicle in a forward direction to a speed which will cause the control system to sequentially upshift through each of the four forward ratio gears. When the shift lever is placed in drive, the control system connects the torque converter driven shaft to the output shaft through the first speed ratio gear in the following sequence: 1) synchronizer flange 60a is moved slightly to the left by an appropriate actuator (not shown) to effect a frictional connection of the
first gear 44 toshaft 40, wherebyshaft 40, which is disconnected from the output shaft, is pulled up toward synchronous speed withgear 44; 2) Flange 60a will then move further to the left andclutch gear 44 toshaft 40 by the jaw clutch in the synchronizer when the synchronous speed is reached; and 3)Clutch 48 is then actuated by pressurized fluid. First gear is now fully engaged. - When engine load decreases and vehicle speed increases to predetermined amounts, the torque converter driven shaft is connected to the output through the second speed ratio gear in the following sequence:
- 1) Synchronizer flange 96a is moved slightly to the left by an unshown actuator to effect a frictional connection of the
second gear 76 toshaft 72, wherebyshaft 72, which is disconnected from the output shaft, is pulled up toward synchronous speed withgear 76; - 2) Flange 96a will then move further to the left and
clutch gear 76 toshaft 72 by the jaw clutch in the synchronizer when the synchronous speed is reached; - 3)
Clutches shaft 40 and drivingly connectshaft 72; and 4) Flange 60a is then moved back to its neutral position to disengage the synchronizer. Second gear is now fully engaged and first gear is disengaged. In the foregoing sequence in upshifting to second gear, it should be noted thatshaft 72 is synchronized withgear 76 through a drive connection with the transmission input and while drive is through the first gear andshaft 40. Such synchronizing may be characterized as input synchronizing. The other ratio gears and the associated countershafts are synchronized in a like manner. - When engine load decreases and vehicle speed increases to a predetermined amount,
bypass shaft 13 is then connected to the output shaft through thirdspeed ratio gear 46 in a four step sequence similar to the above sequence for second gear: 1) Flange 60a is moved slightly to the right to frictionally connectgear 46 toshaft 40; 2) When synchronous speed is reached, flange 60a moves further to the right to engage the synchronizer jaw clutch; 3)Clutches - The sequence for upshifting to fourth gear should be obvious from the foregoing and it should suffice to say that
synchronizer 74 is actuated to the right,clutches synchronizer 42 is disengaged. - Downshifting from fourth gear is merely the reverse of the upshift sequence in that the next lower ratio gear is first synchronized with its respective shaft while drive continues in the higher ratio, the drive is then switched from one countershaft assembly to the other by deactuating and actuating the fluid actuated
clutches - Assuming now that the vehicle operator wishes to move the vehicle in the reverse direction, the shift control lever is placed in the reverse position, whereby the control system will connect the torque converter driven shaft to the output shaft through
reverse gear 80 andidler assembly 108. The sequence of events to effect drive in reverse may vary; one sequence which may be automatically effected by the control system is as follows: 1) Torque converter drivenshaft 26 is pulled down to a low speed by momentarily effecting a driving connection to the output shaft throughcountershaft assembly 36; this is done by connectingfirst gear 44 toshaft 40 and momentarily actuating clutch 48 in the manner described for forward drive in first gear; and 2)Clutch member 118, of theclutch assembly 84, is then resiliently moved leftward byactuator 156 to effect interengagement of jawclutch teeth 118a and 116. - The position of
first gear 44 oncountershaft 40 andreverse gear 80 oncountershaft 72 allows the vehicle operator to power shift between first and reverse. Such power shifting is accomplished by moving the shift control lever between drive and reverse and by programming the control system to momentarily delay or leave reverse clutch 84 engaged and then actuating anddeactuating clutches - Looking now at a feature provided by the arrangement of the helical teeth of the gears in the transmission, it is well known in force analysis of gears having meshed helical teeth that forces acting on the contacting teeth of each gear may be resolved into tangential, radial, and axial components. The tangential force component is useful since it serves to rotate the driven gear. The radial and axial force components on the other hand are not normally useful; they merely add to bearing loads and tend to bend the shaft that the gear is mounted on.
- Looking now at the schematic illustration of FIGURE 5, therein is shown gears 44, 46, and 68 which are mounted on
countershaft 40. These gears are provided with helical teeth which are arrayed with a helical hand such that the bending moments imposed onshaft 40 by axial force components acting ongears shaft 40 to a level less than would be caused if the gears had the opposite hand. More specifically, gears 44, 46, and 68 rotate counterclockwise when viewed from the left end ofshaft 40.Gears gear 68 is a drive gear. The radial forces frl, fr2, and fr3, acting on these gears all act in the indicated directions and tend to bend or bow the simply mountedshaft 40 upward. To counter the bending forces of frl, fr2, and fr3, gears 44, 46, and 68 each have left hand helical teeth. Sincegears shaft 40 downward. Sincegear 68 is a drive gear, the axial force fa3 will act to the right, thereby imposing a counterclockwise bending moment ongear 68 which tends to bend or bowshaft 40 downward. Hence, it may be seen that the axial forces subtract from the radial forces to decrease the net bending forces acting onshaft 40. It should be kept in mind that at any given time, only one ofgears gears -
Gears countershaft assembly 38 have helical teeth inclined in the same direction as the gear teeth ofcountershaft assembly 36 and for the same reasons given forshaft 40 ofcountershaft assembly 36. - The preferred embodiments of the invention have been disclosed for illustrative purposes. Many variations and modifications of the preferred embodiment are believed to be within the spirit of the invention. The following claims are intended to cover the inventive portions of the preferred embodiment and the variation and modification within the spirit of the invention.
Claims (6)
and said fourth driven gear is a reverse speed ratio gear.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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EP81105647A EP0040864B1 (en) | 1978-03-06 | 1979-03-03 | Power shift transmission |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US88407878A | 1978-03-06 | 1978-03-06 | |
US884078 | 1978-03-06 | ||
EP81105647A EP0040864B1 (en) | 1978-03-06 | 1979-03-03 | Power shift transmission |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP79100629.9 Division | 1979-03-03 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0040864A2 true EP0040864A2 (en) | 1981-12-02 |
EP0040864A3 EP0040864A3 (en) | 1983-01-19 |
EP0040864B1 EP0040864B1 (en) | 1986-05-28 |
Family
ID=26081061
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP81105647A Expired EP0040864B1 (en) | 1978-03-06 | 1979-03-03 | Power shift transmission |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP0040864B1 (en) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0088184A2 (en) * | 1981-12-16 | 1983-09-14 | Eaton Corporation | Synchronizer engagement control |
EP0110538A2 (en) * | 1982-11-04 | 1984-06-13 | Eaton Corporation | Automatic transmission with extended range |
EP0212182A1 (en) * | 1985-08-22 | 1987-03-04 | Dr.Ing.h.c. F. Porsche Aktiengesellschaft | Transmission for a motor vehicle |
GB2209060A (en) * | 1987-07-29 | 1989-04-26 | Massey Ferguson Mfg | Transmission including indepedent drive line bypassing torque converter |
DE3917579A1 (en) * | 1988-05-31 | 1989-12-07 | Fuji Heavy Ind Ltd | AUTOMATIC TRANSMISSION FOR MOTOR VEHICLES |
EP0412069A1 (en) * | 1989-08-01 | 1991-02-06 | IVECO FIAT S.p.A. | Hydromechanical power-shift transmission for motor vehicles, particularly for commercial vehicles |
US5782144A (en) * | 1995-08-26 | 1998-07-21 | Jcb Transmissions | Vehicle transmission |
WO2004076888A1 (en) * | 2003-02-25 | 2004-09-10 | Volvo Construction Equipment Holding Sweden Ab | Motor vehicle transmission |
WO2006061054A1 (en) * | 2004-12-11 | 2006-06-15 | Voith Turbo Gmbh & Co. Kg | Transmission assembly |
CN116618909A (en) * | 2023-07-24 | 2023-08-22 | 四川省第一建筑工程有限公司 | Steel construction welding adjusting device |
Citations (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2519279A (en) * | 1944-11-09 | 1950-08-15 | Dana Corp | Transmission mechanism |
DE935047C (en) * | 1948-10-17 | 1955-11-10 | Rudolf Dr-Ing Franke | Multi-stage gear shift gearbox with only two main slip clutches on the drive side |
FR1108127A (en) * | 1954-05-11 | 1956-01-09 | Hydromechanical gearbox | |
US2739487A (en) * | 1952-02-19 | 1956-03-27 | Eaton Mfg Co | Multiple speed transmission |
US2772581A (en) * | 1951-02-10 | 1956-12-04 | Zahnradfabrik Friedrichshafen | Transmission for motor vehicles |
US2787167A (en) * | 1951-03-07 | 1957-04-02 | Zahnradfabrik Friedrichshafen | Change speed gear |
DE1052768B (en) * | 1953-10-30 | 1959-03-12 | Zahnraederfabrik Augsburg Vorm | Hydromechanical compound transmission |
US3001413A (en) * | 1957-06-26 | 1961-09-26 | Daimler Benz Ag | Transmission including disengaging clutch construction |
GB955907A (en) * | 1962-07-11 | 1964-04-22 | Beteiligungs & Patentverw Gmbh | Hydraulic-mechanical multispeed power transmission, particularly for motor vehicles |
FR1401383A (en) * | 1964-04-22 | 1965-06-04 | Engrenages Minerva S A | Improvements to transmissions of the gearbox type, especially for high powers |
FR88466E (en) * | 1965-06-25 | 1967-02-10 | Engrenages Minerva S A | Improvements to transmissions of the gearbox type, especially for high powers |
US3377876A (en) * | 1964-12-24 | 1968-04-16 | Voith Getriebe Kg | Change gear transmission |
US3442155A (en) * | 1966-11-02 | 1969-05-06 | Gen Motors Corp | Countershaft transmission |
US3541885A (en) * | 1969-01-16 | 1970-11-24 | Ford Motor Co | Power shift transmission for racing vehicles |
DE2451739A1 (en) * | 1974-10-31 | 1976-05-06 | Torwegge Maschf F | Handling device for taking a frame from a press - and placing it on a transport belt has two support brackets with a grip on each |
-
1979
- 1979-03-03 EP EP81105647A patent/EP0040864B1/en not_active Expired
Patent Citations (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2519279A (en) * | 1944-11-09 | 1950-08-15 | Dana Corp | Transmission mechanism |
DE935047C (en) * | 1948-10-17 | 1955-11-10 | Rudolf Dr-Ing Franke | Multi-stage gear shift gearbox with only two main slip clutches on the drive side |
US2772581A (en) * | 1951-02-10 | 1956-12-04 | Zahnradfabrik Friedrichshafen | Transmission for motor vehicles |
US2787167A (en) * | 1951-03-07 | 1957-04-02 | Zahnradfabrik Friedrichshafen | Change speed gear |
US2739487A (en) * | 1952-02-19 | 1956-03-27 | Eaton Mfg Co | Multiple speed transmission |
DE1052768B (en) * | 1953-10-30 | 1959-03-12 | Zahnraederfabrik Augsburg Vorm | Hydromechanical compound transmission |
FR1108127A (en) * | 1954-05-11 | 1956-01-09 | Hydromechanical gearbox | |
US3001413A (en) * | 1957-06-26 | 1961-09-26 | Daimler Benz Ag | Transmission including disengaging clutch construction |
GB955907A (en) * | 1962-07-11 | 1964-04-22 | Beteiligungs & Patentverw Gmbh | Hydraulic-mechanical multispeed power transmission, particularly for motor vehicles |
FR1401383A (en) * | 1964-04-22 | 1965-06-04 | Engrenages Minerva S A | Improvements to transmissions of the gearbox type, especially for high powers |
US3377876A (en) * | 1964-12-24 | 1968-04-16 | Voith Getriebe Kg | Change gear transmission |
FR88466E (en) * | 1965-06-25 | 1967-02-10 | Engrenages Minerva S A | Improvements to transmissions of the gearbox type, especially for high powers |
US3442155A (en) * | 1966-11-02 | 1969-05-06 | Gen Motors Corp | Countershaft transmission |
US3541885A (en) * | 1969-01-16 | 1970-11-24 | Ford Motor Co | Power shift transmission for racing vehicles |
DE2451739A1 (en) * | 1974-10-31 | 1976-05-06 | Torwegge Maschf F | Handling device for taking a frame from a press - and placing it on a transport belt has two support brackets with a grip on each |
Cited By (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0088184A2 (en) * | 1981-12-16 | 1983-09-14 | Eaton Corporation | Synchronizer engagement control |
EP0088184A3 (en) * | 1981-12-16 | 1984-11-14 | Eaton Corporation | Synchronizer engagement control |
EP0110538A2 (en) * | 1982-11-04 | 1984-06-13 | Eaton Corporation | Automatic transmission with extended range |
EP0110538A3 (en) * | 1982-11-04 | 1985-07-31 | Eaton Corporation | Automatic transmission with extended range |
EP0212182A1 (en) * | 1985-08-22 | 1987-03-04 | Dr.Ing.h.c. F. Porsche Aktiengesellschaft | Transmission for a motor vehicle |
US4771648A (en) * | 1985-08-22 | 1988-09-20 | Dr. Ing H.C.F. Porsche Aktiengesellschaft | Change-speed transmission for a motor vehicle |
GB2209060A (en) * | 1987-07-29 | 1989-04-26 | Massey Ferguson Mfg | Transmission including indepedent drive line bypassing torque converter |
GB2209060B (en) * | 1987-07-29 | 1991-07-24 | Massey Ferguson Mfg | Vehicle drive lines |
GB2220998A (en) * | 1988-05-31 | 1990-01-24 | Fuji Heavy Ind Ltd | Motor vehicle automatic transmission including two countershafts |
DE3917579A1 (en) * | 1988-05-31 | 1989-12-07 | Fuji Heavy Ind Ltd | AUTOMATIC TRANSMISSION FOR MOTOR VEHICLES |
GB2220998B (en) * | 1988-05-31 | 1992-04-15 | Fuji Heavy Ind Ltd | Automatic transmission for a motor vehicle |
DE3917579C2 (en) * | 1988-05-31 | 1995-03-09 | Fuji Heavy Ind Ltd | Automatic transmissions for motor vehicles |
EP0412069A1 (en) * | 1989-08-01 | 1991-02-06 | IVECO FIAT S.p.A. | Hydromechanical power-shift transmission for motor vehicles, particularly for commercial vehicles |
US5782144A (en) * | 1995-08-26 | 1998-07-21 | Jcb Transmissions | Vehicle transmission |
WO2004076888A1 (en) * | 2003-02-25 | 2004-09-10 | Volvo Construction Equipment Holding Sweden Ab | Motor vehicle transmission |
US7213480B2 (en) | 2003-02-25 | 2007-05-08 | Volvo Construction Equipment Holding Sweden Ab | Motor vehicle transmission |
WO2006061054A1 (en) * | 2004-12-11 | 2006-06-15 | Voith Turbo Gmbh & Co. Kg | Transmission assembly |
CN116618909A (en) * | 2023-07-24 | 2023-08-22 | 四川省第一建筑工程有限公司 | Steel construction welding adjusting device |
CN116618909B (en) * | 2023-07-24 | 2023-09-26 | 四川省第一建筑工程有限公司 | Steel construction welding adjusting device |
Also Published As
Publication number | Publication date |
---|---|
EP0040864A3 (en) | 1983-01-19 |
EP0040864B1 (en) | 1986-05-28 |
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